JPS62282200A - Air-conditioner for vehicle - Google Patents

Abstract

PURPOSE:To maintain the fan efficiency at a high level by functioning means for increasing/decreasing the wind path angle while interlocking with the operation of an air-conditioning mode switching means. CONSTITUTION:A widening angle adjusting plate 3 is provided as means for increasing/decreasing the wind path angle while contacting against the circumferential wall at the downstream area of the wind path in a casing 1. An air- conditioning mode switching means 50 moves the widening angle adjusting plate 3 through a wire 9 and a rotary force transmission means 8. Consequently, the operating point of fan is moved automatically such that the fan efficiency is at the optimal level under any air-conditioning mode thus improving the fan capacity.

Description

[Detailed description of the invention] 3. Detailed description of the invention [Industrial application field] TECHNICAL FIELD The present invention relates to air blowing failure of an air conditioner for an automobile.

[Prior art 1] Since the heating and cooling heat exchangers installed in the air conditioning duct have considerably large ventilation resistances, it is difficult to determine how much of the conditioned air introduced into the dow 1 through the air intake port is skewered. The ventilation resistance σ to the air passing through the duct varies considerably depending on whether the air is passed through these heat exchangers.

In general equipment, the air blowing capacity is variable. l1llit
When the capacity selector switch is set to "high" (if set to "keep", the pendillator bypasses the heating heat exchanger). In the heater and Anoros 1-blowout air conditioning mode, it is around 55 mmAq, and the calm in each air conditioning mode is 450 m3r' h and 350 m, respectively.
1/h) has been actually measured.

[Problems to be Solved by the Invention] 10 Problems to be Solved by the Invention
The resistance coefficient of the duct as a ratio of loss is directly proportional to the total pressure before blowing trt+L and inversely proportional to the square of the wind ♀, so this characteristic value varies depending on the f+- initial state of the air conditioner. The fan efficiency of a wind blower is directly proportional to the product of the blowing pressure and the wind velocity.
It is inversely proportional to the fan's air flow $.

To that end, conventional air conditioners operate in a heater or defrost air conditioning mode (PFI), which has a high ventilation resistance, and also in a penderation air conditioning mode, which has a relatively low ventilation resistance, to achieve the highest fan efficiency. I can't say 1. The efficiency of the fan in one of the air conditioning modes had to be reduced.

The present invention provides an air conditioner for an automobile with an air blower that does not reduce the fan efficiency to the highest possible level in any of the air conditioning modes: ventilation, heater, and defrost. purpose.

[Means for Solving the Problems 1] In order to achieve the above object, the automatic vehicle air conditioner according to the present invention incorporates a centrifugal blower having a scroll casing and selectively connects a plurality of air outlets. Automotive air conditioning system 1.:d3 equipped with an air conditioning mode switching means for switching the air conditioning mode by opening and closing the scroll casing, the air conditioning mode switching means being interlocked with the operation of the air passage angle increasing/decreasing means in the scroll casing and the air conditioning mode switching means. In addition, a configuration is adopted that includes interlocking means for adjusting the Tateki Nagiji expansion angle increasing/decreasing means.

[Operations and Effects of the Invention] The air conditioner for an automobile according to the present invention having the configuration as described above operates the Nagiji-Kiributsu damper, which constitutes the air conditioning mode switching means IM, to control the air conditioner in the scroll casing of the blower. The road widening angle increasing/decreasing means work in conjunction, and the operating point of the feeder is moved to automatic adjustment so that the fan efficiency is maximized under any air conditioning mode.

Since fan efficiency is the sum of the effectively extracted wind power and the human power applied to the Noan rotation shaft, this ratio can be maintained at a high level under any air conditioning mode.
This means that the degree to which a part of the input power is lost as a result of air flow, or that the air pressure decreases due to air resistance is kept to a low level. January noise will be reduced.

[Example] The configuration of the automotive air conditioner according to the present invention will be specifically described below based on the example shown in the drawings.

Figures 1 to 5 show an example device, and as shown in Figure 3, which is a schematic side sectional view, the entire device is constructed using a centrifugal blower (a number of A outlet ports 1b are used for air conditioning). Dak 1-B
1 is read directly to the air inlet end 20a of the air inlet end 20a.

A centrifugal HQ fan 2 driven by a pump 12 is housed in a fan casing 1 that has a scroll shape, and an outside air intake is opened at the top of an inside/outside air switching box 20 assembled to the intake port 1a. First and second internal air intake ports 2 provided opposite to each other in the mouth 21 or side wall portion
The outside air or the air inside the car is taken in from either 2 or 23. 24 and 25 are connected via a link structure (not shown), and a first
and a second C outside air switching damper.

The fan casing 1 is made of hard synthetic resin or metal and has a scroll shape, and is made of J5, which is used to fasten the upper casing 1A and the 1st part casing IB, which are separated at a dividing line provided on the peripheral wall. It is combined by 2G. Then, in the gauging 1 equipped with the discharge river air path a of the compressed air that expands in a spiral shape, an increase or decrease in the air path widening angle is applied to the peripheral wall surface of the downstream acid portion of the air path.
A spread angle adjustment plate 3 as a T' stage is incorporated.

The spread angle gA node plate 3 is made of a metal plate or a synthetic resin plate, etc., which has a sharp shape. The upper and lower ends of )7 are fitted into shaft holes provided in the top wall surface and bottom wall surface of the casing 1, respectively, to rotate around this rotation @4.

In addition, on the peripheral wall surface of the air passage 1 and flow part of the fan casing 1,
The expansion angle adjustment plate 3 widens the air passage expansion angle to the maximum 11]
A bulging portion 1C is formed to prevent the plate surface of the plate 3 from becoming an obstruction to the air passage by matching the inner wall surface of the casing 1 when the plate 3 is in the position shown in FIG. A plate 3 is installed on the bottom of the casing 1 to maximize the angle of Nagiro expansion.
11. ) The height is 2 to 3 m to define the narrowing point r.
A stopper 6 as an arcuate protrusion of 1 liter or less is provided integrally with the casing 1.

A plate reinforcing bar 7 is attached to the other side edge of the expansion angle adjustment plate 3, and this bar 7 has a rotation angle of 1 for rotating the plate 3 around its rotation all 4. A rotational force transmission member 8 for transmitting force is connected. In this embodiment, the member 8 is in the form of a small plate,
The upper end of the bar 7 is inserted into the shaft hole 8a drilled on the H side.
The plate 3 has one end connected to the air conditioning mode switching lever 45 provided on the operation panel 50 of the air conditioner which forms part of the air conditioning mode switching means. A wire 9 for remote rotation operation is connected as an interlocking means.

10 is a cover tube for holding the wire 9.

The curvature of the expansion angle adjusting plate 30 is made to match the curvature of the wall surface of the casing at this point when the fan casing 1 is housed in the bulging portion 1C. In order to narrow the spread angle of the scroll-like air passage a, the wire 9
When the plate 3 is pushed out in response to the movement of the air conditioning mode switching lever 45, the plate 3 rotates to a position where its advance is blocked by the arc-shaped stopper 6, and due to the inherent elasticity of the plate, the stopper 6 with a narrower curvature moves. Since it is bent into an arc shape, both side walls of the narrowed air passage are given a smoothly continuous scroll shape. The arcuate stoppers are also symmetrically provided on the top inner wall surface of the fan casing 1.

The operation panel 50 of the air conditioner is generally built into the driver's instrument panel, and includes, in addition to the air conditioning mode switching knob 51, a lever knob 52 for adjusting the temperature inside the conductor, a lever knob 53 for switching between inside and outside air, and a lever knob 53 for switching between inside and outside air. A lever knob 54 for changing the rotation speed of the 11111 motor 12 is provided.

Rotation 1 rotation 4 by operating the air conditioning mode switching knob 51
5a 17) The lever 45 that rotates has ventilation, heat, and def.
In order to transmit the above operating force to a linkage mechanism (not shown) for interlocking the 38 selective opening/closing damper groups 39 to 41 in a predetermined interlocking relationship,
Another remote control wire 15 is connected. 16 is a duplex serving as a support cover for this wire. 5
However, the wire 15 may not be attached directly to the lever 45, but may be branched from the middle of the wire 9.

Here, regarding the expansion angle of the air passage a17) in the fan casing 1 having the scroll shape of the centrifugal air blower 11A, the fifth
This will be explained with reference to the figures. A centrifugal force is generated on the blades of the fan 2, which has started a high-speed circular motion with the activation of the fan motor 12, and the air to be conditioned sucked into the inner space of the fan from the suction port 1a is moved in the direction indicated by the arrow (toward the arrow shown in the figure). The air is blown out after being pressurized in the air path a in a direction as shown in FIG.

Now, a virtual extension line (
The point where E) intersects with the outer peripheral surface of the fan 2 is defined as (A), and the extension of the radius of the fan 2 at the position of the clockwise rotation angle θ° using the point (A) as the reference point. Let the intersection of the line and the wall surface of the fan casing 1 be (b), the intersection with the expansion p adjustment plate 3 be (), and the intersection with the outer peripheral surface of the fan 2 be (d).

When the plate 3 is brought into contact with the inner wall surface of the fan casing 1 and the expansion color of the air path a is maximized, the air path expansion angle α at the rotation angle θ° is determined by points (b) and (d). It is expressed as the intersection angle of the tangents to the curved surface drawn respectively. In addition, when the plate 3 is brought into contact with the stopper 6 to minimize the divergence angle, the air passage divergence angle β at the same rotation angle θ° is the same as that of the curved surface at points (C) and (D). It is expressed as the intersection angle of tangent lines.

In this implementation, in the ventilation air conditioning mode where the ventilation resistance is relatively small, the ventilation angle α is set to
The value of is 7°, and in the heat and defrost air conditioning modes where the ventilation resistance is relatively high, the angle of the air passage expansion angle β that can produce the maximum fan efficiency is 5°.

As shown in Fig. 3, the air conditioning duct 8 is provided with evaporators 31 and 11 for use as cooling heat exchangers, etc., in order from the upstream side inside the duct body 20, which is made of hard synthetic resin or the like. A heater core 32 as a drought-type heat exchanger, a cold air passage 33 for bypassing this heater lower, a bypass passage damper 34, and an air mix chamber 35 for mixing cold and hot air.
is provided.

At the air outlet end of the duct body 20, there are a ventilation outlet 36, a heat outlet 37, and a defrost outlet 38.
are provided, and each outlet is connected to each outlet grille 36a, 37a, and 38a facing toward the interior of the vehicle.
are communicated with each other through extension ducts for each outlet. 3
9.40. and 41 are a group of dampers for switching air conditioning modes, which together with the device operation panel 50 constitute air conditioning mode switching means, for selectively opening and closing the air outlets 36 to 38 to change the air conditioning state in the vehicle interior. Links that are not shown in the diagram; are said to have a specific interlocking relationship through some structure. This link mechanism is connected to the knob 5 of the air conditioning mode switching lever described in r'iu, which is built into the driver's instrument panel.
It can be rotated by manipulating 1.

Next, four operations of the apparatus of the above embodiment will be explained. First, let's look at the fan characteristic graph (see Figure 7) that represents the air blowing characteristics. Now, let's say that the wind claw at the leaf exit of the winding tower is Va, the total pressure (feed m) is Δp, the fan rotation speed is N, the fan drive torque is Ō, the circumferential speed of the fan is u2, and the outer diameter of the fan is D2. , the flow coefficient φ, the pressure coefficient ψ, the fan efficiency ηr, and the resistance coefficient, and the above-mentioned numerical values hold the following relational expression.

φ"Va/Di ・u2 ψXΔp/u≦ y) foc■a-Δp/T-N k =, Φ/φ2 1<ocΔp/■a2 And the air conditioner connected to the discharge port of the conventional feeder J!lli The fan characteristic graph when the ventilation resistance of the duct B is varied can be schematically drawn as shown in Fig. 7. In this graph, the vertical axis shows the pressure coefficient ψ or the fan efficiency ηr, and the horizontal axis shows the pressure coefficient ψ or the fan efficiency ηr. The flow coefficient φ is taken on the axis. Graph D
is a pressure curve showing the relationship between air volume and wind pressure, and graph E is a fan efficiency curve showing the relationship between wind cooling and fan efficiency.

Further, based on the above relational expression, the l[tfA curves F and G of the air conditioning duct B, which represent the relationship between wind resistance and wind pressure resistance, can be drawn superimposed on the above graph.

Graph F is a graph for the heat and defrost air conditioning modes in which the ventilation resistance in the duct is large, and graph G is a graph for the penderation air conditioning mode in which the ventilation resistance is relatively small.

Then, the intersection points a and b of the pressure curve and the resistance curves F and G are at each of the ventilation halls! 'lThe dynamic oil condition becomes the operating point. In this case, in the heat and defrost air conditioning mode in which the operating point a is located in a region where the flow coefficient φ is relatively small, the fan efficiency ηf is)? The fan efficiency reaches a lower level at point C, which is near the peak of the fan efficiency curve E, and the maximum fan efficiency is reduced by 1q, whereas in the pendeletion air conditioning mode, the much lower level shown at point d is reached. Only fan efficiency can be obtained.

On the other hand, regarding an air conditioning system in which an air conditioning duct B is connected to the outlet to the air outlet which incorporates means for increasing or decreasing the kite path spread angle in the scroll casing, the spread angle in the downstream area of the air path is When fan characteristic graphs similar to those described above were drawn with two settings, 5° and 7°, the graph shown in FIG. 8 was obtained.

Graphs H, I, and J are pressure curves, fan efficiency curves, and curves, respectively, drawn when the air path divergence angle is 5 degrees and the air conditioning mode is set to heat or defrost.
is a generalized curve, and the operating point is located at e.

In the graph, L and M are the pressure curve, fan efficiency curve, and resistance curve, respectively, drawn when the air passage expansion angle is 7 degrees and the ventilation air conditioning mode is set, and the angular moving point is 9. Located in

Here, FIG. 7 is a fan characteristic graph of an air conditioner with the conventional air blower (mA) installed, and the air blower (mA) according to the present invention.
When compared with FIG. 8, which is a graph of the characteristics of air conditioners assembled with +-+, clear differences emerge as shown below.

That is, the former exhibits almost the highest fan efficiency in the heat and defrost air conditioning modes as described above, but the fan efficiency drops considerably in the ventilation air conditioning mode, whereas the latter according to the present invention exhibits almost the highest fan efficiency in the heat and defrost air conditioning modes. By setting the air passage expansion angle in the fan scroll casing to 5° in the heat and defrost modes, a fan efficiency close to the maximum level (1 point) can be obtained at the operating point e, and the By changing the road widening angle to 7°, the fan efficiency (point h), which is close to the maximum level, can be achieved at the operating point of 19°.

In other words, in the heat and defrost air conditioning modes where the resistance coefficient k of the blower increases, by narrowing the divergence angle of the air path, the 1/l @ point is moved to the area where the flow coefficient φ is small and the maximum fan efficiency can be obtained. On the other hand, in the ventilator air conditioning mode where the resistance coefficient k is small, a method is proposed in which the operating point is moved to fAVi with a large flow coefficient φ where the maximum fan efficiency can be obtained by widening the air passage expansion angle. If adopted, it becomes possible to always move the air blower 111A to 1/1 with substantially maximum fan efficiency during any air conditioning mode, and the intended purpose of the present invention is achieved.

FIG. 6 shows the air blow fighting portion of the device of the second embodiment, which uses an air passage expansion angle adjustment plate with a groove structure, which is assembled differently from the first embodiment.

The main body portion of the air passage expansion angle adjustment plate 3 is a rectangular plate bent into an arc shape in the same manner as between the surfaces, and one side edge of the main body portion has a pair of wedge-shaped engagement pieces 3a that function as a hinge portion.
and 3b are integrally formed, and the fan casing 1
By inserting this engagement piece into the insertion hole 1d drilled in the F'lTh part of the bulging portion 1C, the plate 3 is rotated in the direction of the plate surface using the engagement pieces 3a and 3b as fulcrums. be able to.

The other side edge of the plate 3 is provided with a hole 3C for the insertion of a wire 9 for remote rotation manipulation, and the wire 9 is inserted into the plate by screwing a nut 11 into the threaded portion at the tip of the wire A7-9. It is quickly linked to 3.

As for how long the air passage expansion angle adjustment plate 3 should be provided on the back of the go/thread part of the rolled air passage a of the air passage A, it is determined that Determine based on experiments depending on the horn 7's ventilation properties and ventilation stakes.

Furthermore, various methods other than the above-mentioned embodiments are of course possible regarding the shape design of the plate 1- for assembling the air passage expansion angle adjustment plate 3 into the fan casing 1 and the means for rotating the plate 3.

In the above embodiment, the centrifugal air blower (the air outlet A is connected to the air intake end 20a of the air conditioning ducts 1 to B, but any point between the air inlet end and the outlet end of the duct B) You are also free to join.

In addition, as a means for interlocking the air conditioning mode switching means and the air passage expansion angle increasing/decreasing means, instead of the remote control wire shown in the figure, the electricity transmitted in conjunction with the operation of the air conditioning mode switching means (operation controlled by No. It is also possible to use a servo motor or various types of actuators.

[Brief explanation of the drawing]

Figures 1 to 5 show the device of the first embodiment, and Figure 1 shows the plane of the blower with the upper casing removed, the operation panel of the air conditioner, and the means for increasing and decreasing the divergence angle of the air passage. The interlocking mechanism with the air conditioning mode cutting foil means is each schematically shown. Figure 2 is an exploded view of the ventilation hall, Figure 30
Figure 4 is a schematic side sectional view of the entire installation, Figure 4 is a side sectional view of the air outlet 1, and Figure 5 is a side sectional view of the air outlet. FIG. 6, which is a 111m plan view, is an exploded view of the blower of the second embodiment. Fig. 7 and Fig. 8 are graphs showing the fan characteristics of the conventional blower +n incorporated in the automatic ton air conditioner (0 equipment) and the blower according to the present invention. casing) 2...Fan 3...Air passage expansion angle increasing/decreasing means (spreading angle adjustment plate) 6...Stopper of plate 3 7-10.45...Interlocking means 9...Wire for remote control 20... Air conditioning duct 20a...
・Air population end 32.32...Air conditioning heat exchanger 36
...Hebration outlet 31...Heat outlet 38...Defloss 1-outlet 34.39-41
... Air path switching damper 50 ... To the air conditioning mode switching means (operation panel of the air conditioner) ... Send J! II
B...Air conditioning duct fee L! I! , person Kenji Ishiguro Figure 2 Figure 4 Figure 5 Figure 6 Figure 7 *Revised (φ) Figure 8 Flow rate staff! (+25)

Claims (1)

[Scope of Claims] An air conditioning system for an automobile that incorporates a centrifugal blower having a scroll casing and includes an air conditioning mode switching means for selectively opening and closing a plurality of air outlets to switch the air conditioning mode, wherein the scroll casing An air conditioner for an automobile, comprising: means for increasing/decreasing the divergence angle of an air passage within the vehicle; and interlocking means for operating the means for increasing/decreasing the divergence angle of the air passage in conjunction with the operation of the air conditioning mode switching means. .